Hydro-pneumatic spring unit



May 8, 1962 Filed Deo. 24, 1958 R. P. 0G DEN HYDRO-PNEUMATIC SPRING UNIT 5 Sheets-Sheet 1 May 8, 1962 R. P. oGDr-:N

HYDRO-PNEUMATIC SPRING UNIT 5 Sheets-Sheet 2 Filed Dec. 24, 1958 NWN.

4 1 INVENTOR.

Ma'y 8 R. P. OGDEN I'IYDRO-PNEUMATIC SPRING UNIT 5 Sheets-Sheet 3 Filed DeC. 24, 1958 INVENTOR.

R. P. OG DEN I-lYDRO-PNEUMATIC SPRING UNIT May s, 1962 5 Sheets-Sheet 4 Filed DSO. 24, 1958 IN VENTOR.

May 8, 1962 R. P. OGDEN HYDRO-PNEUMATIC SPRING UNIT 5 Sheets-Sheet 5 Filed Deo. 24, 1958 'l llllllllll l f In Il :k

05 2 mn m d 1 Il r y #a lli [l Il .J 20 a, o 6 3 2 4M n w w 4 INVENTOR.

Patented May 8, 1962 3,033,552 HYDRG-PNEUMATIC SPRING UNIT .Ralph I. Ugden, 7522 Walnut St., Hammond, Ind. Filed Dec. 24, 1958, Ser. No. 782,875 12 Claims. CL 267-1) My invention relates to a hydro-pneumatic spring unit that is especially adapted for use in connection with vehicular suspensions, though it has other applications.

More particularly, my invention relates to a suspension device that contemplates a gas spring provided with hydraulic damping.

Until recently, automotive vehicular suspensions have consistently been largely confined to leaf and/or coil steel springs. Such springs are notoriously bulky and heavy and are not adaptable for practical adjustment to account for varying static load conditions; moreover, they require external devices for damping.

However, air springs, which use the elasticity of air for a spring, have now come into limited use. Air springs permit adjustment for changing loads, but they still require accessory damping devices or shock absorbers and are undesirably large in size. r

A principal object of my invention is to provide a hydropneumatic spring that overcomes the shortcomings of both steel and air springs.

A further principal object of my invention is to provide asusp-ension unit that combines a gas spring with hydraulic damping or snubbing.

Yet another important object of the invention is to provide a spring unit which eliminates sliding seals or seals that engage sliding or moving surfaces, thereby eliminating leakage difficulties.

Still a further object of the invention is toprovide a spring unit which contemplates the use ofair spring structures as liquid-filled shock absorbers, the latter cooperating with a novel gas charged device to provide in one unit a gas spring with hydraulic damping that is readily adjusted to account for changes in static load, temperature, and the like.

Other objects, uses or advantages will be obvious or become apparent from a consideration of the following detailed description and the application drawings.

In the drawings:

FIGURE l is a longitudinal sectional view through a preferred embodiment of a spring unit arranged in accordance with the principles of my invention;

FIGURE la is a fragmental sectional view illustrating a modification of the device of FIGURE l;

FIGURE lb illustrates on an enlarged scale, a further modification of the device of FIGURE 1;.'

FIGURE 2 is a diagrammatic plan View illustratingthe unit of FIGURE 1 incorporated in a vehicular` suspension system according to the principles of my invention;

FIGURE 3 is a diagrammatic plan view, partially in section, illustrating still another modification of the device shown in FIGURE l;

FIGURE 4 is an enlarged View, partially in section, illustrating a levelling valve that may be employed in the vehicular suspension shown in FIGURE 2;

FIGURE 5 is a side elevational view of a tractor seat suspension in accordance with my invention;

FIGURE 6 isa fragmental elevational view taken from the right hand side of FIGURE 5;

FIGURE 7 is a diagrammatlc View illustrating I the manner in which the device of FIGURE l may be charged in readying same for use;

FIGURE 8 is a sectional view through the regulating valve ofthe suspension of FIGUREl 5, illustrating its principal components;

FIGURE 9 is a sectional View through a valve fitting employed in the arrangement of FIGURE 7; and

FIGURE l0 is a longitudinal sectional view illustrating the principles of my invention applied to a piston-type hydraulic shock absorbing device. l

General Description Referring now more particularly to FIGURE 1, reference numeral 10 generally indicates a preferred spring unit arrangement in accordance with the principles of my invention. Spring unit 10 comprises a hydraulic spring levelling chamber 12, a two-compartment captive gas or spring chamber 14, and a hydraulic damping chamber 16 that is closely `associated with hydraulic damping cell 18.

The two-compartment gas spring chamber 14 is defined by rigid tubular member 22 and resilient diaphragms 24 and 26 that are positioned across the bore 28 of tubular member 22. In the illustrated arrangement, the respective diaphragms 24 and 26 are clamped to the ends of the tubular member 22 by dished rigid members 30 and 32, respectively, that are drawn up against the tubular member 22 by appropriate bolts 34.

Thus, the levelling chamber 12 is defined by diaphragm- 24 and dished member 3G, while the chamber 16 is defined lby diaphragm 26 and dished member 32.

InV accordance with my invention, the spring chamber 14 is formedinto gas reservoir compartment 36 and gas spring compartment 38. In the embodiment illustrated,

this is done by fixing plate or disc 40 within the bore of v tubular member 22 in any suitable manner, as by Welding. Plate or disc 40 is provided with an 4orifice 42 of capillary dimensions (.as, for instance, having a diameter on the order of .002 to .006 inch), or alternatively, is made relatively thick and is provided with a plug 41 of sintered metal V(see FIGURE la)` or other suitable substance, that is sufficiently porous to provide limited communication between the sides 44 and 46 of disc 40. Furthermore, a

suitable valve 43` (see FIGURE lb) may be employedv i effect, the spaces 56 and 58 on either side of the member 48 comprise a single gas compartment 38.

The hydraulic levelling chamber 12 is placed in com munication with an appropriate source of hydraulic liquid under pressure (depending lon the use to which unit 10 is put) which is admitted thereto through port 60 formed in dished member 30 which may be covered by screen plate 62 formed with suficient openings to readily 1 admit the hydraulic liquid.

The hydraulic damping chamber 16 is placed in oommunication with hydraulic'cushion cell 18 by orifice 64 formed in dished member A32; orifice 64 may be covered by a suitable screen plate '.66 that is similar to plate 62.

The cushion cell 18 in the embodimentof FIGURE 1 is of the rol-ling diaphragmV type including pedestal member 7d which in effect defines part of the damping charn- I ber 16, rolling diaphragm member 72, and tubular retaining member 74.

The pedesta-l member 70 is provided valves 76 and 78 to restrict the llow of hydraulic'iiuid f between chamber 16 and the hydraulic cushion cell.

with hydraulic'liquid through appropriate valve 82. In accordance with my invention, the gasV charge in the with damping Y 3 chamber 14 and the hydraulic liquid charge in the charnber 16 and cushion cell 18 are captive charges in that they are sea-led against escape.

In operation, chambers 12, 14, 16 and cushion cell 18 are charged with suiiicient quantities of the respective fluids indicated to adapt the spring to support a predetermined static load at a predetermined level -or elevation. The device is then placed between a load that is to be supported and its supporting framework, which respectively bear against the dished housing member 30 and the opposite end of the device, which in the embodiment of FIGURE 1 is represented 4by plate 15@ of tubular diaphragm securing member 74 of cushion cell 13.

When the charges in chambers 12, 14, 1'6 and the cushion cell are properly proportioned, the diaphragm 26 will be positioned approximately as shown when a predetermined statie load will lbe supported at its predetermined height. When the load increases, the composite spring structure 81 formed by dished member 30, tubular member 22, dished member 32, and pedestal 70 will move downwardly (in the showing of FIGURE 1) with respect to tubular diaphragm supporting member '74. This will cause a downward rolling action of the diaphragm 72, which will decrease the volume that the hydraulic liquid in the cushion cel-l can occupy, with the result that a consequently increased pressure will open damping valve 78 to permit hydraulic liquid to move into chamber 16 through orifice tid. The increased volume of hydraulic liquid in chamber 16 deflects diaphragm 26 upwardly (in the showing of FIGURE l) against the compressed gas in chamber 14 to further compress same.

The increased static load may be restored to its predetermined height position by forcing additional hydraulic liquid into the chamber 12 by means of a suitable pump. The pumping action continues until the diaphragm member 2 6 is restored to the position of FIG URE. l. During this pumping action, the increase in quantity of hydraulic liquid in chamber 12 detlects diaphragmA 241 downwardly against the captive gas in chamber 14, which compresses it to the point that diaphragm 26 will be restored to its position of FIGURE 1 against the increased pressure that has been applied to chamber 16; this restores the cell 16 to its initial position by forcing sufficient hydraulic liquid through valve 76 te raise the pedestal and the structure it carries to the initial or predetermined position.

When'the static load is decreased, the pressure of the gas in chamber 14 causes hydraulic liquid in chamber 16' to pass through valve 76 and into cushion cell 1 8, which tends to move pedestal 70 and the members carried by it upwardly (in the showing of FIGURE 1) of the tubular diaphragm connecting member 74. Diaphragm 26 will then be deected downwardly by the pressureof the gas in chamber 14.

The load is returned to its desired position by pumping sutlicient hydraulic liquid from chamber 12 to restore the diaphragm 26 to its initial position; as hydraulic liquid is pumped from chamber 12, the pressure in chamber 12 is reduced, which permits the captive gas charge of chamb er 14 to deect the diaphragm, 24 upwardly. At the same time, diaphragm 2 6 moves back to the position of FIGURE l, hydraulic liquid being forced by the weight still supported to flow through valve 78 and into chamber 16, whereby the load is lowered back downto its desired elevation, which is achieved when the diaphragm 26 is positioned as shown in FIGURE 1 It will be appreciated that the unit may be usedl upright as it is shown in FIGURE l, or reversed, the operation being substantially the same. The device may also be used when horizontally disposed or, for that matter, in any desired position. lRegardless of how the unit .10. is mounted, suitable provision can be made for operating and protecting valves 80 and 82.

FIGURE 2 of the drawings illustrates my spring unit incorporated in a vehicular suspension system generally v absorbers.

indicated at 90. The spring units are generally indi cated by reference numeral 10 in FIGURE 2.

In the embodiment of FIGURE 5, my spring unit is shown incorporated in a tractor seat suspension 94, the spring unit being indicated by reference numeral 1t) in FIGURE 5.

The spring unit shown in FIGURE 3 is substantially identical to that shown in FIGURE l except that the cushion cell 162 is separated from the remainder of the unit and connected to the chamber 16a by a condui 16M. Cell 12 is of the bellows type, though it is charged with hydraulic liquid, together with chamber 16 and conduit 104, instead of air as is customary with devices of the lbellows type illustrated.

The embodiment of FIGURE 10 comprises a pistontype hydraulic cushion cell 11d, the remainder of the structure being identical to that shown in FIGURE l.

Specific Description Referring again to the embodiment of FIGURE l, the dished members 39 land 32., tubular member 22, disc dil, and dished member 48 may be formed from any suitable material such as steel. Spring chamber 14 is charged with a moisture-free gas such as nitrogen, while chambers 12 and 1d, and cushion cell 18 are charged with an appropriate grade of low-pour point mineral oil, such as the type used in conventional hydraulic shock Diaphragms 261 and 25 may be formed from any suitable resilient material, such as neoprene rubber or its equivalent or other materials that will be resistant to attack by the specilcfhydraulic liquid employed.

Dished lmembers 3G and 32 may be of any appropriate shape though it is desirable that they be outwardly dished and curved for strengthening purposes. They may be flat plates if suitably lbraced and lformed or mounted to provide the volume desired for chambers 12 and 16; the-term dished lmembers as employed in the claims is intended to include such an arrangement. Screen plate 66 of plate 32 may be eliminated and bore 64 widenedto the diameter 0f pedestal 70 without affecting the function of the spring, but the illustrated arrangement makes for convenience in charging and protects the diaphragm 26 against accidents.

lIn the embodiment of FIGURE l, the dished member 30 is provided with a block-like fitting 12% formed with passages 122 rto which conduit 124 (that feeds to a source of hydraulic liquid) is suitably connected. However, other suitable fittings may be employed as may seem necessary or desirable. Y

rrl`he valves Sil and 82 may be of any suitable type,`

the ball and threaded stud 128. Head portion may receive an appropriate @P1131 (see FlGURES 5 and 10i) provided with seal 133 to close ot the respective valves.

Screen plates 6.2 and 66 may be of any suitable type, though their perforations should be suiciently large and numerous to freely pass the hydraulic liquid. They are provided to prevent the respective diaphragms from being drawn through the respective passages or Vperforations 6l) and @d under adverse pressure conditions.

The valves 7 and 73 each comprise a stern 14.0l having heads 142 and 143 at each end thereof. The respective stems arebiased to their positions of .FIGURE l by appropriate compression springs 144- interposed between Y the respective heads 143 and the plate member 145 that ing action provided by these valves may be varied by varying the compressive forces applied by springs 144.

The heads 142 of the respective stems 14!l are lifted ofi their seats by pressure acting on their stem or inner sides (when the necessary pressure diierential exists).

The cushion cell 1S includes base plate 15b bolted to lange 152 of tubular diaphragm retaining device 74 as by appropriate bolts 154. Of course, a hydraulic seal should be effected between plate 150 and flange 152.

Tubular diaphragm retaining device 74 is formed with an internal shouider 156 that is engaged by the external shoulder 1.58 of diaphragm 72. rihe other end of the diaphragm 72 is given a shape generally complementary to the pedestal 71B. Diaphragm 72 may be provided with reinforcing bands or wires 164iv and 162 if so desired.

The two-compartment gas chamber 14 is of particular significance. As mentioned hercinbefore, the disc d@ divides this chamber into reservoir compartment 36- and spring compartment 38. The orilice 42 must be of capilJ lary dimensions to restrict gas ow between compartments 36 and 3S and its equivalent, plug 41, must provide a similar restricted gas flow. The gas ow permitted by oriice `112, plug 41 or valve 43 should be suiciently gradual so that when the unit is taking a series of rapid jolts, the springing action is provided by the air that is in compartment 38 without significant loss ofair through orifice i2 (or plug 41).

Valve 43 comprises a body 159 (see FIGURE lb) secured in plate 4i) and positioned in compartment 38.

Body 43 is formed with valve seats 161 and 163 each,

provided with a groove 165 of capillary dimensions; ball 167 when forced against either seat 161 or 163 permits only a slow flow of gas through the seat groove l16S until the pressure equalizes in yboth the compartments and 38. Rapid build up of pressure in either compartment 36 or 33, as on bouncing, causes a fast air flow which forces the ball 167 against an unseating stem 169 of T-shaped members 171 and acts primarily as a check valve, said slow gas ow in the meantime passing through the adjacent grooves 165. Screen plate '-173 may be provided over opening 175 of valve 43, and compression springs 177 act on members 171.

It may be mentioned that when hydro-pneumatic device 1@ is functioning as a spring, the restriction 42, plug 41 or valve 43 are of necessity not completely effective in blocking or preventing iiow of gas between compartments 3e and 33. These are sufficiently etfectve for the purposes of the invention, however, for the reason that a complete spring cycle requires very little time, about .92 second, for the spring shown in FIGURE l when used, for instance, as in `FIGURE 5 as a tractor seat sus-V pension. A cycle includes movement, for instance,V of composite part S1 down from static position, up past static position and then back down to static position;` During this cycle, the pressure will be the same in cornpartment 3d as in compartment 36 at the start of the cycle at static position, increasing in compartment 38 as the spring structure 81 travels downwardly, decreasing i-n compartment 33 as composite structure 81 travels upwardly and equalizing with that in compartment 36 when it goes by the static position (and decreasing as it continues upwardly of static height). As composite structure 81 start downward again, the pressure in compartment 38 again increases until at static height it again is equal to the pressure in compartment 36. The pressure in compartment 33 is thus greater than in compartment 3o for half the cycle and less for half the cycle. l The pressure diterential, which determines the amount of gas transferred through oriiice 12, builds up from zero (at static height) to `an amount depending upon the deflection from static height, the volume of spring compartment 38, the eiiective area supporting the load, `and the pressure of the gas in compartment 38 at static height or position.

For instance, it will require about 293 p.s.i.g in unit 10 to support a 200 pound man at static height on the seat suspension 94. The pressure would build up in compartment 3d inl a downward deflection of 1/2 inch, to 405 p.s.i.g. yAn upward deflection of 1/2 inch would decrease the pressure in compartment 38 to 211 p.s.i.g. There is a relatively small amount of time at such pressure differentials for passage of gas between compartments 38 and 36, so that actually an unimportant Aamount is transferred duri-ng a spring cycle. While it is possible to mount time delay check valves between compartments 36 and 38, substituting for the orifice 42 the plug 41 or valve 43, the design complications so introduced would not appear to warrant the small improvement thereby resulting.

in View of the fact that the unit i151 is designed to support a static load at a standard height, which means that at such standard or predetermined height the diaphragm 26 will be in a predetermined position, for instance, the position of FGURE l, the compartment 38 forms a gas compartment of predetermined volume which is maintained effectively constant `during the operation of the device, as when the vehicle of FGURE 2 is in motion, the compartment 36 forming a storage space for gas that must be added to or removed from chamber 38 to dispose the diaphragm at its predetermined position. As the unit 1t? is adapted to be levelled to a predetermined elevation or height, the springing action provided by unit 15)' when supporting a load at such predetermined height or elevaticnfwill be uniform regardless ofthe load imposed upon it.' Excess gas passes through oririce 42 (or plug 41 or valve-"43) if the load is increased above or is reduced below the predetermined amount. The same action occurs on increases or decreases in temperature.

The embodiments of FiGURES l, 1a and lb provide orifices of capillary dimensions yand the language em ployed in the appended claims is intended to cover the structure of these figures and their equivalents.

It will be appreciated that the unit 10 mustl be charged in such a manner that the diaphragm 26 will 'bevv at the desired position when the unit is under a predetermined static load and thus will hold, for instance, the body of the vehicle shown in FIGURE 2 at a predetermined elevation. Furthermore, some manner of recharging inthe field or at the service stations to replace fluid lost from slow leaks is desirable. The arrangement of FIG- URE 7 has been provided for this purpose, though it is to be understood that other apparatus and methods may *be employed as mayv seem necessary or desirable by those skilled in the art.

" pump 178 and a charging valve fitting 182 that is adapted for connection with hydraulic charging valve 82, and an appropriate conduit 184 terminating in a nozzle or spout 186 from which hydraulic liquid may iiow into a graduated container 183 of any suitable type.

Conduit 180 should be provided with a check valve 192 of any conventional type and a pressure gauge 194; conduit 184 should be provided with an appropriate type of oi-on valve 196.

As indicated in FGURE 9, the valve tting 182 is provided With a tubular stud 260 carrying collar 201 adapted to screw-threadedly engage thread head i of a valve 82. Tubular stud 200 screw-threadedly carries plunger 262 provided with handle 204 for turning same against ball 134 to lift same on? its seat. Fitting 182 may be provided with an appropriate packing seal 296 about plunger v202 which is pressed into sealing relation therewith -by cap 208 turned against packing gland 210. Seal 203 may be interposed lbetween the end of stud 200 and head 130 of valve S2.

In operation, the apparatus is employed as follows: First of all, the gas chamber 14 is charged through valve ng d 8G with an appropriate gas to about one-half of the required nal charging pressure. 'l'hen the charging valve fitting 182 is applied to the valve 32 (after unit 1d is turned upside down) substantially as shown in FIGURE 9, or in any other suitable manner, and cion valve 196 moved to `the E position. The plunger 262 is then operated to move ball 134 ot its seat and pump 17S is started to pump hydraulic liquid from reservoir T72 into the charnber 16 and its associated cushion cell 18. When the space within cushion cell 18 and chamber 16 has been iilled with hydraulic liquid, continued operation oi pump 173 will deiiect diaphragm 126 upwardly (in the showing of FIGURE 1) until it is forced into contact with baci: stop plate 48. At this point, the pressure gauge 19d will show a sudden rise in pressure, at which time the pump 17S should be stopped. y

Off-on valve 196 is then opened slowly to permit hydraulic iluid to leave spout 136. The flow from nozzle 186 will for a time contain air bubbles, and as soon as a steady stream of liquid without bubbles emerges from nozzle 186, valve 196 should be closed; if the liquid flow stops before the stream is free of bubbles, the valve 195 should be closed and the previously mentioned steps repeated.

With the valve 196 `again closed, the liquid in container 188 should be returned to reservoir 172, after which the container is then returned to the position of FIGURE 7. The pump 178 should again be operated until the pressure gauge 19d again shows the sudden rise in pressure at which time the pump should be stopped. Valve 1% is then opened to permit a predetermined amount of liquid to iiow into the graduated container as determined by'the graduations of the container. Valve ld should then be closed and valve iitting 182 removed.

The predetermined amount of liquid returned to the container will be that amount necessary to restore the diaphragm 26 to the position of FIGURE 1, or any other desired standard position,

The chamber lo and cushion cell t3 of the unit are now charged with a measured amount of hydraulic liquid, and the gas charge is then completed to the desired predetermined pressure.

The above procedure may be *followed whether or not levelling chamber l2 has a charge; it preferably is given at least a partial predetermined charge to keep the stress on diaphragm 24 at a minimum. This charge may be applied -to chamber l2 in any suitable manner.

On recharging of chamber 16 and cell 1S at service stations or the like in the eld, apparatus such as that indicated `at 170 in FIGURE 7 may be employed to add hydraulic liquid until the pressure gauge Md indicates the sudden rise in pressure at which time the pump 173 is Y stopped. Valve 196 is `then opened to permit the discharge of a predetermined amount of hydraulic liquid necessary to lrestore diaphragm 26 to its predetermined standard position.

When a gas recharge is desired, the hydraulic liquid should be drained from the chamber 16 and then the gas `and liquid charging procedure originally mentioned above.

should be repeated.

The unit of FIGURE 3 `is functionally the same as that of FIGURE 1 and includes chambers i211, 14a and ida that are formed from structures essentially the same as described in connection with the embodiment of rFIG- URE 1. Like reference numerals are employed to indicate similar parts in FiGURE 3 (as well as the other i 8 manner to end plates 2?5 and 217, which the load and its support actually engage.

It may also be mentioned that, if desired, the two compartments of chambers 14 or ida may be remote from each other and connected by a conduit that includes oriiice means of capillary dimensions.

The unit 229 of FEGURE l() differs from that of FIG- URE l by the use of the piston-type cushion unit iii). Thus, the unit 220 includes chamber 316 of the embodiment of FIGURE l, the dished member 32 thereof i'xedly carrying piston-forming member 222. The pistonforming member 222 is slida'bly engaged by suitable packing elements 226 that in the illustrated embodiment are V-shaped in crosssectional configuration and which `are compressed between packing rings 228 and 23d by retainer 232 screw-threadedly engaging the cylinder-form ing member 224.

The cylinder-forming member 22d should be provided with a pierced lug 234 or any other suitable structure that permits this member to be pivotally mounted, as well as a valve 32 for charging purposes.

The device 220 operates in substantially the same manner as the device 16 through the sealing action carried by the cushioned cell is not `as eective as cushion cells 13.

Referring now to FIGURE 2, the suspension system for the` velrice incre-.des four units to mounted be Ieen the i ective wl els of the vehicle and the hassis that 4 .di ,ariiy inciudes longitudinally extending frame members 254 that carry the vehicle body (not shown). The units l@ may be associated between the wheels and the frame structure in any conventional man- .er, such as now us'cd for the conventional air springs. E24 read to leveiling valves 253s of the type atically illustrated in FEGURE 4. In the show- .nr-GURE 2, a single levelling valve 256 is provided at the front of the car while two leveiling vaives 256 are provided at the rear of the car. The leveiiing valves may be secured, tor instance, to a vehicle body between t vehicle body and the ground engaging wheels in any manner, they each including an actuating arm 250 h in the case of the forward levelling valve 252 is connected to a stabilizer bar 262 whiie in the case of the two rear levciiing valves o, is connected to an axle strut these conventional automotive components being shown only diagrarnmatically.

The leveliing vaines 256 are connected by hydraulic liquid supplying conduits 21%, 258, 27d, 272 and 274 to anappropriate type of hydraulic pump 276 that is carried 'ie autcrnobiie and actuated by the automobile motor, as by a pulley belt engaging appropriate pulley 273.

W' pump draws hydraulic liquid from an approi .ereservoir to supply it to the respective chambers when needed, as dictated by the positioning of the reveiling valves 256.

Return conduits 262, 235i, 236 and 233 return hydraulic lisuid from the respective levelling values to reservoir .T when this action is dictated by the respective lcveiling valves.

A bypass conduit 295i including check valve 292 ot any approriate type interconnects the supply and return conduits .74 and so that during normal operation of the vehicle at its predetermined elevation, the pump 276 may continuousiy operate to return hydraulic liquid to reservoir.

specific levelling valve 25a shown in FGURE 4 generaiiy comprises a body portion 3th? carrying a closed 352 in which stub shaft 3M is journalled in any Y manner to pivot about axis Stub shaft 31% is xed to arm and within chamber 3532 carries orojection L @n clockwise movement of stub shaft 364, pin 310 is moved downwardly of FIGURE 4 to open orice 312 to admit hydraulic liquid from pump 276 to conduit 12d of the associated spring unit 10.

Gn countercloclcwise movement of stub shaft 304, projectionV 39S engages pin 314 to displace ball 31rd 4trom its seat and permit return of hydraulic liquid from the associated unit lil to, for instance,-.a return conduit 286.

Balls 316 and 3% are held in their illustrated positions by appropriate compression springs 320 and 322 while the head 324 of pin 3l@ is held against orifice 3l2 by appropriate compression spring 326.

The levelling valve shown in FIGURE 4 is intended to be the forward .levelling valve 256 of FIGURE 2, link 331i being connected to stabilizer rod 262.

The specific levelling valve employed is not critical althrough the specific valve shown in FIGURE 4 has the important feature of the ball checks sealing oil the iluid under pressure, thereby permitting very little loss of liquid wherrthe vehicle is not in operationA Being pressure sealed, there is no dependence on close tolerances to prevent leakage from chamber ,12pt the associated unit 19.

Normally the levelling or height control valves 256 are designed so that there is a dead band of operation about plus or minus one-quarter of an inch from the normal or designed height within which there is to be no ow to or from the spring unit lil. The Valves 255 are automatic in operation and are provided for the purpose of directing additional hydraulic liquid to the respective spring units when the vehicle is below the normal or design height, and to bleed ofi liquid from the spring units when the vehicle is above the normal or design height. Such conditions prevail mainly when the vehicle is jouncing or rebounding when absorbing irregularities of the highway, upon a change or load as when passengers are entering or leaving the vehicle, or when luggage is added or removed, upon temperature changes, which would change the pressure oi the gas in the spring unit, thus requiring compensation, and when the vehicle is going around a curve where centrifugal force places additional weight on the outside wheels.

The actual size of the specific units 1i) as employed in the iront and rear of the vehicle will be etermined by conventionalconsiderations of vertical distance to be travelled and weight to be supported. The hydraulic system shown in FiGURE 2 may also include a conventional accumulator device to store up hydraulic liquid under pressure against a gas for use under conditions of heavy ,demand for adjustment, as Where several passengersenterthe Vehicle. Accumulators are common components of hydraulic systems so no specific illustration is believed necessary.

The seat suspension 94 of FIGURE 5 may be employed for tractor seats or seats of other vehicles or apparatus wherein a passenger or operator is to be supported against jounce and rebound. The unit is mounted in any suitable manner on the vehicle floor 35i?` (as by resting on blocks 351) and the hydraulicliquid is supplied to or removed from the chamber 12 by a lhydraulic system similar to that shown in FIGURE 2, but including regulator valve 352 in place of lthe levelling valves 256. .A suitable pump 354 actuated by the vehicle motor supplies hydraulic liquid under pressure to supply conduit 356 which is connected to regulating valve 352; hydraulic liquid is returned from the yvalve 352 to reservoir 353 by appropriate return conduit 369. Supply conduit 356 and return conduit 365 may be connected by appropriate bypass conduit 362 including check valve 354` to permit continuous operation of motor v354, which may be operated by an appropriate pulley belt engaging pulley 366.

Adjacent cushion unit yllii of seat suspension 94, a pair of spaced supports 37@ are secured in any suitable manner to the tops of which are respectively mounted appropriate bearings 372 which journal shaft 373 that iixedly carries spaced` seat support bars or members 374 to which the tractor seat 376 is secured in` any suitable manner.

Each member 374 carries a headed pin 378 to which is pivotally connected a depending support bar 380 that is fixed as by welding to the dished member 30 of the unit 1i).

The seat supporting members 374 include angled projections or extensions 382 which project between stop bars 384 and 386 that define. the maximum and'minimum compression of the unit lil. Supports 370 may-be rein- Iforced by appropriate braces 388 or in any suitable man-` ner. Y

The unit 10 is initially charged as described above and then applied in the position shown in FIGURE 5. When the rider climbs into seat 376, he operates the regulating valve 352 to raise or lower the seat to the predetermined elevationl that provides the predetermined resiliency de- Sired regardless of the operators particular weight.

As indicated in FIGURE 8, when operating arm 390 is swung to the right of FIGURE 8, projection 392 which is iixed to operating arm 390 goes downwardly to engage pin 394 and move ball 396 from its seat within the valve body 398. Hydraulic liquid then will ilow from supply conduit 356 through passages 400, 402, 404, past ball check Valve 406 and through passages 468 and 410 to conduit 412 that'corresponds to conduit 124 of `FIGURE 1 and extends between valve 352 and the unit 10.

On movement of the handle 390 tothe left of FIGURE 8, projection 414,- which is xed to handle 390, contacts pin 416 which throws ball 418 oil of its seat and permits hydraulic liquid to return from unit 10 throughv conduit 412, passages 41d, 42d, 422, 424 and thence to return conduit 36o and reservoir 358.

Balls 396, 406 and 418` are pressed against their respective seats by appropriate compression springs 426, plugs 428 closing the chambers 430 in which the respective balls 406 and 418 are disposed.

Pins 394 and 416 are each provided with an annular flange 432 which respectively rest on shoulders 434 of caps 438. The respective pins are sealed against leakage by appropriate 0ring seals 436 positioned in caps 438.

It may be added that the modified spring units shown in FIGURES 3 and l() may be substituted for the specic units shown in FIGURES 2 and 5. And alternatively, unit 10 may be positioned to the right of shaft 373l by extending supporting members 374 and inverting unit l0 for application against a suitable abutment above supporting members 374, without altering the leverage obtained.

The spring unit 14) as employed inV seat suspension 94 is designed to operate at a static pressure on the order of 147 p.s.i.g. for a 10() pound person up to pressures on the order of 441 p.s.i.g. for a 300 pound person. conditions, the pressure will be the same in all the spring unit chambers, but when absorbing vertical movement,

pressure differentials `will occur that will equalize when Static conditions return. When the composite spring structure 81 moves downwardly or toward cushion cell member 74, the pressure of the liquid below plate will be greater than above it, and when the composite structure S1 moves away from cell member 74, the pressure of the hydraulic liquid above plate 145 will be greater than that below, both conditions being created by the presence of damping valves 76 and 7S. The pressure in chamber 12 and reservoir chamber 36 are equal at all times, as are the pressures of the gas in spring chamber 3S and the liquid above damping valves 76 and 78.

The spring units when employed in suspension system 9) are designed for operating pressures corresponding to the loads they will carry.

Generally speaking, units 10 are designed -for operation under static pressures ranging from 504000 p.s.i. depending on the load to becarried. The vunits have a vibration rate in the range of 35-85 vibrations per minute, which is well under that normally encountered when vehicles hit `bumps or the like. Because of the relatively high pressures involved, there will be little change in vibrating characteristics of a particular unit 10 between its maximum and minimum static pressures.

At static Advantages of Invention It will thus be seen that I have provided a spring unit with hydraulic damping that is compact and leakage-tree. I have found that substantially higher pressures can be employed in my unit than whenrusing air alone as in the conventional air spring devices.k Parts thus may be smaller, cheaper and easier to mount.

Since the gas is sealed into the spring system, there is no problem of moisture, dirt, corrosion or other oxidation involved such as isrencountered with the use of air compressed from the atmosphere. Thus, metal parts can be made of steel.

The spring units herein disclosed have the dual functions of absorbing and damping shock. Without damping, the load carried by the spring would oscillate up and down for numerous cycles, after a shock, before coming to rest. in the arrangement of FIGURE 5, the spring unit serves as a frequency changer in that it converts the higher vibration Vrates applied to a vehicle to slower and less objectionable ones. It is a peculiarity of the human body that slower vibrations with greater amplitude cause much less distress than more rapid vibrations at shorter amplitude,

`and my invention provides such low vibration rates with maximum amplitude.

, The two-compartment gas chamber permits the spring to operate at avirtually constant frequency throughout its load carrying range as variations that might be caused `by load changes and temperature changes are compensated for. This is to be distinguished from conventional units employing a captive gas in a single chamber since these units have a lretmency that is inherently dependent upon the load and the temperature; thus, for instance, temperature decreases and load increases increase the frequency of vibration yby decreasing the volume that the gas can occupy.

Hydraulic pumps adapted for use in connection ywith this invention, as compared to air compressors necessary for the conventional air springs, are much smaller, more etticient, cheaper and more maintenance-free. Furthermore, many contemporary vehicles now have hydraulic pumps (for operating steering, brakes and other accessories), that may be used in practicing my invention. Hydraulic control valves are smaller and easier to maintain in a lealtproof condition than gas valves.

The units herein disclosed can be mounted in any position, which is to be distinguished from `known conventional gas and liquid spring units. This is because the gas and liquid chambers are sealed from each other.

The foregoing description and the drawings are given merely to explain and illustrate my invention and the invention is not to be limited thereto, except insofar as the appended claims are so limited, since those skilled in the` art who have my disclosure before them will be able to make modifications and variations therein without comprising a rigid tubular member having spaced resilient diaphragms xed across the bore thereof to define said chamber, a partition mounted in said chamber and extending across said bore, said partition being formed with orice means of capillary dimensions, a second chamber associated with one end of said tubular member and defined in part by one of said diaphragms, a third chamber associated with the other end of saidltubular member and defined in part by the other ofv said diaphragms, said second -and third chamber being charged with hydraulic liquid, one of said last mentioned chambers being adapted for communication with a khydraulic cushion cell, and means for damping hydraulic How between said one of said last mentioned chambers and said cushion cell.

2. A hydro-pneumatic spring unit comprising a first chamber charged with gas under pressure, said chamber comprising a rigid tubular member having spaced resilient diaphragms xed across the bore thereof to define said chamber, a partition mounted in said chamber and eX- tending across said bore, said partition being formed with orifice means of capillary dimensions, a second chamber associated with one end of said tubular member and defined in part by one of said diaphragms, a third chamber associated with the other end of said tubular member and dened. in part by the other of said diaphragms, said second and third chambersbeing charged with hydraulic liquid under pressure, a hydraulic cushion cell in communi-cation with one of said last mentioned chambers, and means for damping hydraulic ow between said one of said last mentioned chambers and said cushion cell.

3. A hydro-pneumatic spring unit comprising a first chamber charged with gas under pressure, said chamber comprising a rigid tubular member having spaced resilient diaphragms fixed across the bore thereof to deiine said chamber, a partitionrmounted in said chamber and extending across said bore, said partition being formed with oriiice means of capillary dimensions, a second chamber associated with one end of said tubular member and deined in part by one of said diaphragms, a third chamber associated with the other end of said tubular member and defined in part by the other of said diaphragme, said second and third chambers being charged with hydraulic liquid under pressure, means for supplying and withdrawing hydraulic liquid to and yfrom one or" the last mentioned chambers, the other of said last mentioned chambers being in communication with a hydraulic cushion cell, and means for damping hydraulic flow between said other of said last mentioned chambers and said cushion cell.

4. The unit set forth in claim 3 wherein said nrst chamber on the side thereof defined by the diaphragm that in part defines said other oi said last mentioned chambers is provided with back stop means against which the last mentioned diaphragm is adaptedto abut on charging of said other of said last mentioned chambers.

5. A hydro-pneumatic spring unit comprising a rst chamber charged with gas under pressure, said chamber comprising a rigid tubular member having spaced re silient diaphragms tiXed across the bore thereof to dcfine said chamber, a partition mounted in said chamber and extending acrossv said bore, said partition being formed with oriiice means ofcapillary dimensions, a sec' ond chamber associated with one end of said tubular member, said second chamber comprising an outwardly dished rigid member secured to said tubular member adjacent said one end thereof, said dished member and the diaphragm adjacent said one end of said tubular member defining said second chamber, a third chamber associated with the other end of said tubular members, said third chamber comprising an outwardly dished rigid member secured to said tubular member adjacent said other end thereof, the second mentioned dished member and the diaphragm adjacent said other end of said tubular member deiining said third` chamber, thevsecond men tioned dished member being formed with orifice means, a hydraulic cushion cell in communication with the last mentioned oriiice means, said second and third chambers and said cushion cell being charged with hydraulic liquid under pressure, and means for damping hydraulic flow between said cushion cell and said third chamber.

6. The unit setA forth in claim 5 wherein said cushion cell is directly connected to said second mentioned dished member by said second mentioned orifice means.

7. The unit set forth in claim 5 wherein said cushion cell is remote from said second mentioned dished mernber, and wherein conduit means extends between said cushion cell and said second mentioned oritice means.

8. A suspension system for a Vehicle seat comprising a rigid support member pivoted adjacent one end thereof for movement about a substantially horizontal axis and carrying the seat adjacent the other end thereof, a hydropneumatic unit interposed between the vehicle and the support member between the seat and the pivotal mounting of said support member, said unit comprising a rigid tubular member having spaced resilient diaphragms filed across the bore thereof to denne a first chamber, a partition mounted in said chamber and extending across said bore, said partition being formed with orifice means of capillary dimensions, a second chamber associated with one end of said tubular member, said second chamber comprising an outwardly dished rigid member secured to said tubular member adjacent said one end thereof, said dished member and the diaphragm member adjacent said one end of said tubular member defining said second chamber, a third chamber associated with the other end of said tubular member, said third chamber comprising outwardly dished rigid member secured to said tubular member adjacent said other end thereof, the second mentioned dished member and the diaphragm adjacent said other end of said tubular member deiining said third chamber, the second mentioned dished member being formed with orifice means, a hydraulic cushion cell in communication with the last mentioned orifice means, a hydraulic reservoir and pump carried by the vehicle, a hydraulic liquid regulating valve, conduit means extending between said second chamber and said regulating valve, supply conduit means extending between said valve and said pump, and return conduit means extending between said valve and said reservoir.

9. In a hydro-pneumatic spring unit including a gas spring chamber formed in part by one side of a resilient diaphragm, with the other side of the diaphragm forming one side of a hydraulic Achamber that is connected to a hydraulic cushion cell, the method of charging the hydraulic chamber and cell which includes partially charging the air spring chamber with gas, pumping suficicient hydraulic liquid into said cushion cell and said hydraulic chamber to deilect said diaphragm into said spring chamber a predetermined amount, releasing hydraulic liquid from said hydraulic chamber and cushion ceil until the liquid stream is free from bubbles, again pumping suiiicient hydraulic liquid into said hydraulic chamber and said cushion cell to deflect said diaphragm said predetermined amount, withdrawing a predetermined amount of hydraulic liquid from said hydraulic chamber and cushion cell, and further charging said spring chamber with gas to a predetermined pressure.

l0. A hydro-pneumatic spring unit comprising means for defining a first compartment and a second compartment, said means including ia iirst diaphragm defining part of the first compartment and a second diaphragm defining part of said second compartment, said compartments being in communication with each other through orifice means of capillary dimensions, and being charged with gas under pressure, housing means together with said first diaphragm defining ia first hydraulic liquid receiving chamber, further means together with said second diaphragm defining a second hydraulic liquid receiving chamber, said second chamber being adapted for communication with a hydraulic cushion cell, said first and second chambers being charged with hydraulic liquid, and means for damping hydraulic flow between said second chamber and said cushion cell.

l1. A hydro-pneumatic spring unit comprising a first compartment, a second compartment, said compartments being in communication with each other through orifice means of capillary dimensions, each of said compartments being defined in part by diaphragm means, a first hydraulic liquid receiving chamber defined in part by one of said diaphragm means, a second hydraulic liquid receiving chamber deiined in part by the other of said diaphragrn means, a cushion cell in communication with one of said chambers, said cushion cell and said one chamber being charged with hydraulic liquid, the said compartment that is dened by the diaphragm means of said one chamber forming a gas spring of predetermined volume, when the other of said chambers is charged with suilicient hydraulic liquid to dispose the last mentioned diaphragm means in a predetermined position, independently of the load imposed on the `spring unit.

l2. A hydro-pneumatic spring unit comprising a rst compartment, a second compartment, capillary -means for establishing communication between said compartmerits, each of said compartments being defined in part by diaphragm means, a first hydraulic liquid receiving chamber defined in part by one of said diaphragm means, a second hydraulic liquid receiving chamber defined in part Iby the other of said diaphragm means, a cushion cell in communication with one of said chambers, said cushion cell and said one chamber being charged with hydriaulic liquid and including means for sealing said charge against escape, said compartments being charged with gas and including means for sealing said gas charge against escape, the other chamber being charged with hydraulic liquid, and means for varying the volume of the last mentioned hydraulic liquid charge.

References Cited in the file of this patent UNlTED STATES PATENTS 

